Vibration damper for overhead cables



Jan. 10, 1950 L. ROSTQKER 9 -9 VIBRATION DAMPER FOR OVERHEAD CABLES Filed Jan. 22, 1949 2 Sheets-Sheet 1 Low-i5 R 0570702? Jan 10, 1950 1... ROSTOKER VIBRATION DAMPER FOR OVERHEAD QABLES Filed Jan. 22, 1949 2 Sheets-Sheet 2 Patented Jan. 10, 1950 UNITED STATES iOFF'IC'E VIBRATION DAMPER FowovERnEAD {CABLES Louis Itostoker, Toronto, Ontario, Canada Application January 22, 1949, Serial No. 72,247

.10 Claims. 1

This invention relates to vibration damping of overhead cablessby means of.a suppressor appropriately attachedtto the electrical transmission line, and more particularly to a suppressor adapted to introduce into the transmission line a counteracting vibration which Will lessen tendencies toward creation of, mechanical standing waves on the-"transmission line.

An object of this invention is to suppress transverse vertical vibration in transmission 'lines caused by the swaying-ioithe supporting towers.

A further object of this invention is to provide a vibration suppressor which will absorb :the energy of vibration from the transmission line to which it is attached and=which will vibrate itself with a relatively largeamplitude.

A still further object of this iIIVBIItiOmiS TDLDIO- vide a vibration damper for transmission lines which may-be.:.-adjusted -to-have a-resonant frequency of-zvibration-equal tothat of a transmission line supporting'rtower.

A still further object of this invention is to provide a means wherebythe efiective mass of an oscillating body may be increased-Without materially increasing itskweight.

A still further object of this invention is to provide a vibration damper having energy absorption means therein which will render mechanical adj ustmentwof "the iliiamperninnorder .to suit a variety OxC.0nditi0nS,e1 eSS rCritiQal.

All of the foregoing and still further objects and advantages of the invention will. hecomeeapparent from a study of the following specification,-,t;aken in conjunction .with.the.accompanyingdrawings,

wherein like characters of reference indicate corresponding parts throughout theseveral views and wherein:

Fig. 1 is a side elevation in perspective of the device with a portion'thereof 'cut awayin'order to show more clearly the internal construction;

Fig. 2*is' a sideielevationof the device taken on a vertical plane passing through the two supporting posts;

Fig. is a. section pn'the line 3"3 in Fig- '2;

Fig. 4 is a section on the line 4-4 in Fig. 2;

Fig. .-;5...illustratesj: the manner. :in, V. which suppressors, constructed according to this invention, would be attached to a typical transmission line; and

Fig. 6 .is-aschernaticrrepresentation"of the theoretical operation'of thedevice.

Transverse vibration of a transmission line may be initiated'byiagustofiwindstriking a supporting Atower; I thereby 'deflecting "the tower with its supporting insulators in a'directlon parallel to :thattof .thetransmission line. Thismomentary deflection causes a slight slackening-of the'tension in the cable on the leeward side of the tower and adjacent the -insulators'extending therebetween. "isOrdinaryy wave. :motion will thereupon take place and this undulation in the transmission line will proceed atpia"certainuvelocityalong the line in a direction away from the tower which initiated it. ,-.Just, as sound waves'may be refiected from a plane surface when'they impinge thereo-n so -will thisundulation be-refiected back upon itself from. the-.nextssueceeding. tower, eventually reappearing somewhat attenuated at the transmission tower whence-it originated. In the interim, the tower, due to its natural frequency oivibration, will-havereturned to its normallundeflected position and possibly will have initiated manyumoreqsimilar .undulations. With normal transmission lines and towers, the distancebetween towers (i. e. the span), the tension in the cables, the height of the towers, and the design structure of the towers andsupporting members, are suchflthat the natural frequency of vibration of the'ttower-in 'thefdirection of propagation of waves*alongthe-transmission line'is many times greater than'the fundamental-frequency of vibration of: the freely:s,uspended span of wire extending betweenia'djacent'towers. As the directconsequence ofthis,ithewavelength oi the disturbance;propagated. bythe vibrating tower is considerablyshorterthanthe tower to tower span so that the resulting standing Wave upon the line due to reflection from,the-,next adjacent toweris actually close to a high order harmonic of the fundamental frequency of vibration of the trans-- mission line. Hence,\,along the line, there will appear a large number of loops and nodes if the disturbanceris-allowed to build up intomeasurable proportions. wSince vibration of this nature causes fatigue in the conducting cable. it is most desirable that it beiminimized.

This invention discloses a construction of suppressor which is adapted to have.a;.natural frequency of vibration equal to the natural frequency oiavibration-ofithetower. Ehe suppressor is suspended on the transmission line .at a distance from the supporting insulator on the tower equal to of the wavelength of the potential standing=wave onthe line. "The natural frequency of vibration of the suppressor is .thenadjustedito be..-as,nearly asupossible equal to that of the transmission line supporting tower, since the frequency of rthezstandingwaveon the transmission line ,will be equal to the resonanttfrequency of the supporting tower.

In order to explain the theoretical operation of the device hereinafter described in detail, it will be necessary to develop the equations of motion of a coupled system such as that shown in Fig. 6, wherein part (b) shows the system in part (a) in a deflected position, the extent of the deflections being indicated as $1 and :02. As shown in this figure, the extent of the deflection of M (which represents the suspended transmission line) is proportional to the periodic force F sin wt. The spring constants of the suspension-coupling system are represented as K and k and the masses of the system as M and m respectively.

At any instant the forces acting on mass M are:

2 (1) M T the inertia force (2) Kat the spring restoring force,

(3) Ic(:r1m2)1-, the restoring force of the coupler spring, and

(4) F sin wit, the driving force. 7 Clearly, (1)+(2)+(3)=(4) and therefore:

Also, from Fig. 5 it will be seen that the forces acting on the coupled mass m are:

d x (7) m T the 1nert1a1 force, and

may be solved by substituting therein the equations:

(10) m1=a1 sin wt and (11) xz=az sin wt where a1 and as are the crest values of the amplitudes of oscillation of masses M and m respectively.

Substituting (10) and (11) in (6):

d (a sin wt) M a sin wt (k+K)ka sin wt=F sin wt Similarly, substituting in (9) m.d=(a, sin wt) +k(a, sin rot-a sin wt)=0 Substitute Equation 14 in Equation 12 and 15 solve for art From Equation 12 we may write:

2 1e a k(1+ "-)=F+a,k

I k k Substitute Equation 13 in Equation 16:

gangsta f E l'lhAgalngi let (fronifEquation 17) and so:

r .sPrina-constant mass Therefore," the symbols p andZTP represent the natural freguenqy of oscillation, ofjtheucoupled mass systems tic, m, and K; 1M. respectively. ".iIThe result ,of this 'isjthat if the. resonant frequency of the coupleol'system' It mnis chosen .tobe equal to the 'frequencrpfthe.applicdgforce I" (said frequency being w radians per secondlIEquations 15. and 18. are satisfiedso thatlamplitude=ai becomes n mplitudecai .beccmes. a .maximum.

The mass M. has been, used :inlthe'ioregoing theoretical development;to ,repllesentthelefiective mass of a;transmission'lineat.the noint. at .which the device hereinafter full described is attached thereto. The force F sin wt is the periodiciforce which is impresed upon the transmission line.

The frequency of this-lfQrcelw) has been found to be determined by the resonant frequency of the supporting transmission line tower about its .v rti al axis-istanfdin wavesneyebnedunonthe transmissionflinedue to;refiection. of. .waves ,from towerslnextladjacent. theltower whichlinitiated the ,wave tendcto .build upzupomthe-line,-;but1due .to. the attachment of aspring+masssystem (k,. m)

.atthe-efiectiveforce centrerofgthestanding:wave

eon the.-.line,- saidstanding-wave .icaninewerlhuild .up tov an; appreciablevmagnitude,becauselthezenwergy .pthereinds transferred tto 'athe; springemass sy emiknm :so a hflt ithe .latterztakes .011 3111 (the .mot on.wwhichxwould.:normally izhaye aexisted; c on (the;transmissionzline. 51 The :unctlon:.of. the :de- Nice;hereinafter;described 'lsito provide a springcmass system shaving aoperative characteristics substantially' thezsame :as :-the1;hypothet1cal sys- :tem:represented in .the foregoing development as --k,-s mswherein:the saidzdevicewillmperatezzthmughroutaa:widezvarietyzofscondltlons oftwcathersaxfd also whereinptherresonant frequency pfi thessysitem maybe easily; adjusted :so asttoi-besa nearly 7 as possible. equali toxthe:resonantrireqnencyl tithe itransmission; line tower;=near whichi itais xtoabecjat- .tached. The.,saidaresonant:fnequencycof .:.the; sysstemis .va-ried by-altering:theaeffectiveimasmofthe system. without substantially; altering :its'. actual weight.

Referrin r-to :Eigs; :1,:2;and1 :4, taracap r1 legatttachedatovtransmissioniline cables :-(Elg-;-.. by;-=a suitable clamping means designatedcgenerallyras 9. A pair of. :supportingirpostsi l0. nd2l;I-;..:area.at- :tached 1 by means of :nntst f I. 2 .and"; I: respectively to-soap 1, which,: it: will -bezndted,igalsolzfunctmns aspa corona shield. A, shaft '14 sextendsmbetween the lower extremitiesrofvrposts tilt-and llicthessaid shaft carrying thereon :a i'otataiblysmounted zinertia disc 15.

A cupshaped [member 5116 eiszisecnred zbyuneans of angle brackets' 1-1 and vbolts I 8rtto" a .circular plate I 9 haVillg a. diameter; slightlyrlesslthanilthe inside-"diameter of= the cap]. "-Passageszlllaandsil inplate l 9 permit passage therethrough ofposts l0 and ll I Helical springs 2'2aandz23zdispcsedzon posts sand :I l respectively: bear upontcollarsyzl and '25 (whichprovide stopsgfor the. springs): and press upwardly againstlbushingsdfitand izl dislposedupon'the underside of plate tease-caste support 'the body of the device, :said bodysbeingcom-- posed of cup 'lG-andplateilll. 'Assecond pairs sof helical springs--28 and 29 surround posts .1 0 and ll respectively between-plate l s end theunderside of 'cap 1. Springs 22" and 23 -thereforeitend ato work against springs 2 8-= and- 29 so as to" hold the bodymember-in a more central position 'byipressing the plate I 9 upon springs -Z8--and-29 .as-shown 'in-Fig. 2. '='Since--plate Wis therefore-efiectively secured to the helical springsr'it cannot" bounce, and its oscillation will consequently be "substantially sinusoidal.

,Referring to Figs. 1 and 4,;a link'fill connected .byqUrclamprtll to plate l9 is'also coupled atits opposite extremity eccentrically of .inertia lldisc .15.v It willbenotedfromifiig. 31,.that a plurality of positions. may be..,se1ected 0r the pointpat which member :33 may :be secured to. disc .15 relatively'to the axis of rotation oflthe latter. ..'..A

plurality 20f; holes. 32.each. at a .slightlyI-difierent radius fromrthe centre of rQtati0n--.ofldisc -15 are ;provided:therein for that purpose andthe overall purpose of this provision will be subsequentlydescribed.

Inertia disc :1 5. 'has three cweights 33 attached -.to ;it-nean its outertperipherymo that themcment of; inertia ;ofdisc L5-. alooutitsaxis eof rotation-cis considerably increased. nsirrce-adisc ll 5 ,-is cou- 'pled to body plate 9 byrlinkasflrany reciprocation of member [9 withincap"?ktendsztacauserotation of disc l5 about its axis [4. Referring for a moment to Fig. 5, it will be seen that a deflection of the supporting tower34"due to a gust of wind impinging thereon causes a momentary release :of. tension: in transmissionl-linei L8 sand" therefore causes a momentarydepressionxinithe::transmis sion line next. adjacentztowerj'u on theleeward side thereof. This undula'tion indicated in-Fig; "5 as 8 proceeds away-from the transmis'slon line power whence it originated :butwill onl-y -have *travelled a short-distancebefore the-transmission line I supporting tower will have' returned '-'to its original unde'fiected position, once again restoring tension in the'transmission line. Due to refiection of the wave'tl from the next adjacent supporting tower 36, and of course due to continued oscillation of tower 34, a standing wave will develop upon the transmission line extending between towers 34 and 36, the wavelength of the said standing wave being clearly proportional to the resonant frequency of the supporting line tower 34 as previously described. Clearly therefore if the vibration suppressor indicated generally in Fig. 5 as S is attached at a one-quarter wavelength distance from the supporting tower the amplitude of deflection of cap I will tend to be a maximum. In other words, the suppressor will be attached at the effective force centre of the originating vibration. With reference now to Figs. 1, 2, 3 and 4, it will be seen that a momentary downward deflection of transmission line cable 8 (indicated as 8 in Fig. 5), Will cause a downward movement of supporting posts I and II and therefore a similar downward movement of inertia disc I5, all relatively to cup member I6 and cover plate I9 comprising the casing. It will be evident that springs 28 and 29 will be compressed and that springs 22 and 23 will be extended, and that also due to link 30 extending between plate I9 and a hole 32 in the inertia disc I5, the said disc will have rotated about its axis of rotation I4 as shown in Fig. 4.

It should be noted that for the sake of clarity, Fig. 4 is drawn as if cup I6 and plate I9 had moved upwardly to assume the raised position shown therein since this is in effect what really happens when once the system gets underway as (Also, this mode of dean oscillating damper. picting the suppressor in one of its many oscillatory positions lends a certain degree of clarity and simplification to the drawings.) Thus it will be seen that a rotary action is applied to disc I whenever there is relative motion between cap I and the casing. These two coupled bodies (the suppressor casing and transmission line at the point of suspension) comprise a resonant springmass system exactly analogous to the hypothetical system discussed above and represented in Fig. 6. The effective mass m of the oscillating body is a function of the mass of members I8, I9, 3%, 3I and the moment of inertia of disc I5 and weights 33 about axis I4 and is clearly greatly in excess of the mass represented by the sum of the masses of members I5, I6, I9, and 3I. This effective mass may be varied over a considerable range by adjustment of the radius at which link 30 is attached to disc I5. Springs 22, 23, 28 and 29 of course comprise the sole spring means and the combined spring-constant of the springs is exactly analogous of the spring constant It used in the foregoing theoretical development. Therefore, with all these factors known, the suppressor may be designed to have any desired resonant frequency where m is, as outlined above, the effective mass of the oscillating suppressor casing.

It should be noted that fine adjustment of m may be made by altering the amount of oil or other similar fluid 35 which is placed within cup member I6, said oil performing the function of a mass varian as well as a means of continual lubrication and as a damping means upon inertia disc I5 and weights 33. It is desirable that said damping means he provided since the result thereof is analogous to the result achieved when a resistanceis placed either in series or in parallel with an electrical resonant circuit: a decrease in the selectivity of the critical frequency at which the coupled system oscillates at maximum amplitude. Thus, the provision of the fluid damping means, lessens the necessity for precision calculation of the frequencies of vibration of the transmission line tower and/or the suppress ing means, since said suppressing means may then be made to operate over a much broader band of frequencies than would be achieved if damping therein were very small. To put the result in another manner, the provision of such an energy absorption factor as the kinematic viscosity of the oil or other fluid, renders the device less critical in operation and more likely to operate under variable conditions brought about by weather, ageing, and general mechanical variances in tower and suppressor constructions. It is therefore merely necessary that the theoretical frequency of oscillation of the transmission line damper be made as nearly as possible equal to the theoretical frequency of oscillation of the transmission line tower near which it is intended to attach it, in order that satisfactory operation of the device may be achieved.

To return for a moment to the original theoretical development, it will be seen that the resonant frequency of the suppressor may be taken to be that of the transmission line tower and therefore equal to the frequency of the periodic force F applied to the cap and various attachments thereto. The amplitude of vibration of the transmission line, a1, therefore becomes 0, and 0.2 the amplitude of vibration of the coupled mass m becomes a maximum, and therefore body members I6 and I9 oscillate at a maximum amplitude.

It is thought that the construction and use of the invention will be apparent from the above description of the various parts and their purpose. It is to be understood that the form of the invention herewith shown and described is to be taken as a preferred example of the same and that various changes in the shape, size and arrangement of parts may be resorted to, without departing from the spirit of the invention or the scope of the subjoined claims.

What I claim as my invention is:

1. In a damping device including a mechanical spring-mass oscillatory system having a resonant frequency, substantially determinable by the where k is the spring constant and m is the effective mass of the system, a first member adapted to be secured to a body the vibrations of which are to be damped, a second member coupled by a spring to the first member and adapted to oscillate relatively to the first member, means for varying said mass so as to change the resonant frequency of the system the weight thereof remaining substantially constant, comprising an inertia disc rotatably disposed on one member of the oscillatory system, a link connected to the other member of the'oscillatory system and connected eccentrically of the inertia disc, whereby linear oscillatory relative movement of the two said members imparts angular movement to the inertia disc so that themechanical reaction thereof imparts to the linear oscillating member an encasem- 9i effectivermassither"magnitudeirof'i which: may be variethby adjusting 'thezafo'resaid dink;

2'. In a dampin'g'lxievice iricludinga mechanicalsprmgsimass' os'clllatorysystem havingza resonant freimency substantiallydeterminable:by the equalwhere k is the spring constant and m is the effective ma'ss oftl-ie sy'stem; a firstm'ember adapted to be' s'ecured to -a body the vibrations-of which or i-adiai positions eccentrically 'thereof, whereby Iin'ean-"pSciHatory' relative movement of the two said members impart's angular movement to'th'e inertia dise s'o that the mechanical reaction thereor imparts tothe linearlyoscillating member an effectiye -mass thvmagnitude'of" which" may be varied by adjusting the aforesaid link.

a da'mping device includinga mechanicalspring-mss oscillatory system *having' a resonant frequency substantially" determinable by the" equationswhere k is the spring constant and m is the effective mass of the systeme a first member adapted toJoe secured to a body the vibrations of which areitc; bedamped; asecond member coupled b a smlngetotheifirst'unember and adapted to oscil later-relatively" tort'he' first" member, means for" varying: saidmassso' as to change the" resonant" frequencyofi' the system the. weightth'ereof remamingtsub'stantially constant, comprising an mum-m dis'c*"roi,atably' disposed. .on one member" of'the" oscillatory system; a link connected to the oth'enmemb'erofthe oscillatory system and means forconne'cti'n'g the linkto'th'e' disc at aplura'lity offfra'dial" positions: eccentrically thereof, said means-comprising a" plurality of holes inthe disc thrcugnanyLoneloflwhich the link may extend, whereby linear oscillatory relative movement'of thertwo' saidmembersimp'arts angular movement to theinertia'disc' sothat'the mechanical reaction thereofimpartsto" the-linearlyoscillating memberi'an *eflctivemass'the' magnitude of which may bevaried .by adjusting. the aforesaid link.

4? Ir'iadamping'device' including. a mechanical springc-massoscillatory system having a resonant frequencysubs'tantially determinable by the equawhere k is the'sm'mgsconstantmndrmds'the effective massof the system, a first member adapted to bemsecured to a body the vibrations of whichare' were. damped; aplura'lity of'parallel postsisecured to* tne""first-m'ember;' a'se'cond member spring mounted on the said posts, said second member being adapted to oscillate relatively to the first member, said oscillation compressing and extending said spring means, means for varying said mass so as to change the resonant frequency' of. the system the" weight thereof re mainingsubstantially constant," comprising an 'in-- ertia: disc rotatably disposedon the said first member, a link connected'tothe second-member of theoscillatory' system-'and connected eccentrically of 'the inertia"disc,'.whereby linear oscillatory irelative movementof f the: two said members imparts angular movement to theinertia'disc' so that the mechanical reaction thereof imparts to the linearly oscillatingmember an effective mass the magnitude of which may be varied by adjusting the aforesaid link;

51-111 a'damping'deviceincluding a mechanical i spring-mass oscillatory system having a resonant frequencysubstantiailydeterminable by the: equation where his the spring constant and m is the effective-mass of the system, a first member adapted to be secured to a'body-the vibrations of which are to be damped, a pair of parallel posts securedto'the' first member, a second member provided' with=passagesthrough which the posts extend,

a-stop'on each'post, spring means between the stops and the second member forsupporting the second member so that the second member may oscillate longitudinally of' thepoststh'ereby compressing andextending thesprings, means for" varying-said mass so as to "change the resonant frequency of the system the weight thereof remaining substantially" constant; comprising an inertiadisc rotatably 'di sposedon one member of the oscill'atory system; a linkconnected to "the other member of the oscillatory 'systemand connectedeccenti'ically of the inertiadisc, whereby linear'oscillatory' relative movement of the two said memb'ers'irnparts angular movement toth'e inertia disc so that the mechanical reaction thereof imparts to the linearly oscillating member an effective mass the""magnitude of which may be varied by adjusting the aforesaid link.

6: In" a damping deavi'ce including a mechanica'l-spring-ma'ss oscillatory-system having a reson'ant' frequency substantially determinable by the equation where k is the spring constant and m is the effective mass of the system, a first member adapted to 'be secured to a body the'vibrations of which are to'be damped, a'pair of parallel posts secured to the first member, a second-member provided with passages through which the posts extend, a stop on each post below the second member, spring means between the-stops and the second member'for supporting" the second member so that it may'oscillate"longitudinally of the posts therebycompressing'and' extending the springs, a second spring means between the "second memher" and thefi'rst member'to'press' the second member continuously upon the first helical springs in order to reduce non-sinusoidal oscillationof" the second member, means for varying said mass'so' as to change the resonant frequency of tlie system the weight thereof remaining substantially constant, comprising an inertia disc rotatably disposed on one member of the oscillatory system, a link connected to the other member of the oscillatory system and connected eccentrically of the inertia disc, whereby linear oscillatory relative movement of the two said members imparts angular movement to the inertia 7. In a damping device including a mechanical spring-mass oscillatory system having a resonant frequency substantially determinable by the equation where k is the spring constant and m is the effective mass of the system, a first member adapted to be secured to a body the vibrations of which are to be damped, a pair of parallel posts secured to the first member, a second member provided with passages through which the posts extend, a stop on each post, a helical spring on each post resting on the stop and adapted to support the aforesaid second member so that the second member may oscillate longitudinally of the posts thereby compressing and extending the helical springs, means for varying said mass so as to change the resonant frequency of the system the weight thereof remaining substantially constant, comprising an inertia disc rotatably disposed on one member of the oscillatory system, a link connected to the other member .of the oscillatory system and connected eccentrically of the inertia disc, whereby linear oscillatory relative movement of the two said members imparts angular movement to the inertia disc so that the mechanical reaction thereof imparts to the linearly oscillating member an effective massthe magnitude of which may be varied by adjusting the aforesaid link. r

8. Ina damping device including a mechanical spring-mass oscillatory system having a resonant frequency substantially determinable by -the equation where k is the spring constant and m is the effective mass of the system, a first member adapted to be secured to a body the vibrations of which are to be damped, a pair of parallel posts secured to the first member, a second member provided with passages through which the posts extend, a stop on each post below the second member, a helical spring on each post resting on the stop and adapted to support the aforesaid second member so that the second member may oscillate longitudinally of the posts thereby compressing and extending the helical springs, a second helical spring on each post between the second member and the first member to press the second member continuously upon the first helical springs in order to reduce non-sinusoidal oscillation of the second member, means for varying said mass so as to change the resonant frequency of the system the weight thereof remaining substantially constant, comprising an inertia disc rotatably disposed on one member of the oscillatory system, a link connected to the other member of the oscillatory system and connected eccentrically of the inertia disc, whereby linear oscillatory relative movement of the two said members imparts angular movement to the inertia disc so that the mechanical reaction thereof imparts to the linearly oscillating member an cf fective mass the magnitude of' which maybe varied by adjusting the aforesaid link.

9. In a damping device including a mechanical spring-mass oscillatory system having a resonant frequency substantially determinable by the equation JE m to oscillate within the said cap of the first mem ber, means for varying the said mass so as to change the resonant frequency of the system the weight thereof remaining substantially constant, comprising an inertia disc rotatably disposed between the pair of posts and within the cupshaped member, alink connected atone end to the second member and at the other end eccentrically ofthe inertiadisc, whereby linear oscillatory relative movement of the two said members imparts angular movement to the inertia disc so that the mechanical reaction thereof imparts to the linear oscillating member.an effective mass the magnitudeof which maybe varied by adjustingahe aforesaid-,linh- 10. In a damping device including a mechani-, cal spring-mass oscillatory system having a res onant frequency substantially determinable by the equation whrelo is the's'pring constant and m is .the 'effective mass of the system, a first member ada'pted to be secured to a body the vibrations of which are to be damped, a cup-shaped member carrying a quantity of fluid coupled by a spring to the first member and adapted to oscillate relatively to the first member, means for varying said mass 50 as to change the resonant frequency of the system the weight thereof remaining substantially constant, comprising an inertia disc ro. tatably disposed on one member of the oscillatory system and extending into the fluid, a link fective mass the magnitude of which may be l varied by adjusting the aforesaid link, the natural resonant frequency of oscillation of the ,os-,

cillatory systembeing rendered less criticalby the viscosity of the fluid.

REFERENCES CITED The following references are of record in the file of this patent:

' UNITED STATES PATENTS Number Name Date s 989,958 Frahm Apr. 18, 1911 1,995,190

Rostoker 19, 1935 LOUIS Ros roKEa' 

